US6273611B1 - Bearing for spindles in spinning or twisting machines - Google Patents

Bearing for spindles in spinning or twisting machines Download PDF

Info

Publication number
US6273611B1
US6273611B1 US09/412,321 US41232199A US6273611B1 US 6273611 B1 US6273611 B1 US 6273611B1 US 41232199 A US41232199 A US 41232199A US 6273611 B1 US6273611 B1 US 6273611B1
Authority
US
United States
Prior art keywords
bearing
shaft
tube
arrangement according
diameter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US09/412,321
Inventor
Gerd Stahlecker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Novibra GmbH
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Assigned to STAHLECKER, HANS, STAHLECKER, FRITZ reassignment STAHLECKER, HANS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: STAHLECKER, GERD
Application granted granted Critical
Publication of US6273611B1 publication Critical patent/US6273611B1/en
Assigned to NOVIBRA GMBH reassignment NOVIBRA GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: STAHLECKER, FRITZ, STAHLECKER, HANS
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H7/00—Spinning or twisting arrangements
    • D01H7/02—Spinning or twisting arrangements for imparting permanent twist
    • D01H7/04—Spindles
    • D01H7/045—Spindles provided with flexible mounting elements for damping vibration or noise, or for avoiding or reducing out-of-balance forces due to rotation
    • D01H7/047—Spindles provided with flexible mounting elements for damping vibration or noise, or for avoiding or reducing out-of-balance forces due to rotation with springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2340/00—Apparatus for treating textiles
    • F16C2340/18—Apparatus for spinning or twisting

Definitions

  • the present invention relates to a bearing arrangement for spindles in spinning and twisting machines comprising a rotatably supported shaft as well as a bearing housing, a neck bearing, a step bearing and a radially movable step bearing tube, which is arranged in an oil bath, whereby the diameter of the shaft is smaller at the step bearing tube than at the neck bearing.
  • the shaft of standard spindles in the short staple field of practically all makes has a diameter at the neck bearing of approximately 6.8 mm and at the step bearing a diameter of approximately 4.5 mm, at a distance from the center of the neck bearing to the step bearing of 100 mm.
  • These standard dimensions have become established over decades in practice as a presumed optimum. They take into account the fact that the shaft of the spindles must, in the area of the step bearing, be able to move radially to a certain degree, and that in particular the surface pressure at the step bearing must be under control.
  • the sliding bearing clearance in the step bearing is of great importance. Indeed, it would be desirable to reduce the bearing clearance.
  • a reduction in the bearing clearance leads however to an overheating of the step bearing, whereby small bubbles can form in the oil bath and thus lead to an occasional tearing off of the lubricating film.
  • the circumferential speed of the shaft at this point is reduced. Surprisingly, it has been shown that with this measure, bubble formation at the critical point can be avoided.
  • the absolute bearing clearance can hereby be reduced in the desired way, which in turn leads to silenter running of the spindle.
  • the difference in diameter between the shaft and the step bearing tube now measures 0.015 to 0.035 mm, at a diameter of the shaft of approximately 3 to 3.5 mm at this point.
  • the single drawing FIGURE is a side sectional view of a spindle bearing and spindle assembly constructed according to a preferred embodiment of the invention.
  • the vertically arranged spindle 1 of the present invention for example for a ring spinning machine, comprises a shaft 2 driven to rotate, said shaft 2 being supported in a neck bearing 3 in the form of a roller bearing, and in a two-piece step bearing 4 .
  • the neck bearing 3 and the step bearing 4 are located in a bearing housing 5 , which has a closed bottom 6 .
  • the bearing housing 5 essentially comprises a tube 7 containing the bottom 6 , and a bearing head 9 which takes up the neck bearing 3 , which bearing head 9 is inserted from above into the tube 7 by means of a press fit 8 .
  • an oil bath is located in the area of the step bearing 4 .
  • the step bearing 4 comprises a step bearing tube 11 which takes up the radial forces, and a step bearing 10 comprising a thrust plate 12 which takes up the axial forces.
  • the step bearing tube 11 is supported in a centering tube 13 , which in turn is affixed in the bearing head 9 by means of a press fit 14 .
  • the centering tube 13 comprises a helically-shaped recess 15 , which renders the centering tube 13 flexible to a desired degree.
  • annular gap is located, which takes up in a known way an oil spiral 16 .
  • the oil spiral 16 is arranged in its entirety in the oil bath.
  • the annular gap comprising the oil spiral 16 has a connection to the oil bath of the step bearing 4 .
  • the oil spiral 16 is supported upwards by means of a spacing tube 17 .
  • the spindle 1 together with a plurality of further adjacently arranged spindles, is affixed in a spindle rail 19 , denoted only by a dot-dash line, in a known way.
  • a drive wharve (not shown) is further arranged at the spindle 1 , whereby all drive wharves are driven by one drive belt extending in machine longitudinal direction.
  • the bearing shown corresponds to the standard one used in practice.
  • the distance from the center of the neck bearing 3 to the tip of the shaft 2 at the bearing plate 12 measures 100 mm, to the center of the step bearing tube 11 , approximately 94 mm.
  • the diameter of the shaft 2 at the neck bearing 3 usually measures 6.8 mm, the diameter of the shaft 2 just above the step bearing tube 11 , that is before the tapering of the shaft 2 , measures approximately 6.3 mm. Bearing arrangements with these dimensions seemed to be fully developed, as they have been proven many millions of times over.
  • the silent running of the spindle 1 can be improved when the diameter of the shaft 2 in the step bearing tube 11 measures 3 to 3.5 mm maximum.
  • the circumferential speed of the shaft 2 in the step bearing tube 11 can be reduced.
  • a reduced absolute bearing clearance leads no longer to a tearing off of the lubricating film in the step bearing tube 11 .
  • the power required for the drive is reduced at the same time.
  • the shaft 2 at the step bearing tube 11 has a slightly spherical form.
  • step bearing tube 11 in a clamped flexible centering tube 13 in close proximity to the neck bearing 3 is not absolutely necessary for the invention. Rathermore it is alternatively possible, in a way not shown, to arrange the step bearing tube 11 in another radially movable way.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

Spindles of spinning and twisting machines have a rotatable shaft supported in a bearing housing. The bearing housing comprises a neck bearing, a step bearing as well as a radially movable step bearing tube, which is arranged in an oil bath. The diameter of the shaft at the step bearing tube measures at the most six times the diameter at the neck bearing. Preferably, the diameter at the step bearing tube measures no more than between 3 and 3.5 mm. Thus the absolute bearing clearance in the step bearing tube can be significantly reduced, which results in a quieter running of the spindle and to a reduction in power consumption for the drive.

Description

BACKGROUND AND SUMMARY OF THE INVENTION
This application claims the priority of German application 198 65 774.4, filed Dec. 3, 1998, the disclosure of which is expressly incorporated by reference herein.
The present invention relates to a bearing arrangement for spindles in spinning and twisting machines comprising a rotatably supported shaft as well as a bearing housing, a neck bearing, a step bearing and a radially movable step bearing tube, which is arranged in an oil bath, whereby the diameter of the shaft is smaller at the step bearing tube than at the neck bearing.
Bearing arrangements of this type are well known in practice and are described, for example, in the brochure Suessen-Novibra Technical Information SCT.6114 ND. The shaft of standard spindles in the short staple field of practically all makes has a diameter at the neck bearing of approximately 6.8 mm and at the step bearing a diameter of approximately 4.5 mm, at a distance from the center of the neck bearing to the step bearing of 100 mm. These standard dimensions have become established over decades in practice as a presumed optimum. They take into account the fact that the shaft of the spindles must, in the area of the step bearing, be able to move radially to a certain degree, and that in particular the surface pressure at the step bearing must be under control.
For the smooth running of the spindle, the sliding bearing clearance in the step bearing is of great importance. Indeed, it would be desirable to reduce the bearing clearance. With the today standard spindle speeds of 22,000 rpm and more, a reduction in the bearing clearance leads however to an overheating of the step bearing, whereby small bubbles can form in the oil bath and thus lead to an occasional tearing off of the lubricating film.
It is an object of the present invention to improve the above mentioned bearing arrangement in such a way that a smaller bearing clearance than previously known is possible in the step bearing.
This object has been achieved in accordance with the present invention in that the diameter of the shaft at the step bearing measures at the most 0.6 times the diameter of the neck bearing.
By means of reducing the diameter of the shaft at the step bearing, the circumferential speed of the shaft at this point is reduced. Surprisingly, it has been shown that with this measure, bubble formation at the critical point can be avoided. The absolute bearing clearance can hereby be reduced in the desired way, which in turn leads to silenter running of the spindle. Advantageously, the difference in diameter between the shaft and the step bearing tube now measures 0.015 to 0.035 mm, at a diameter of the shaft of approximately 3 to 3.5 mm at this point.
Surprisingly, it has been established that, by applying the above mentioned measure, in addition the required power for the drive is reduced. A reduction of approximately 1 watt per spindle is possible.
In the case of lower spindle speeds, when the hydrodynamic pressure does not take up the bearing load at the step bearing completely, that is, the step bearing acts in the mixed friction area, further improvements of the spindle running can then be recorded when, between the shaft and the step bearing, a particularly narrow bearing gap is created in that the shaft at the step bearing tube is slightly spherical in form. As the shaft has to be ground in any case with a special grinding wheel in this area, the spherical grinding does not lead to a cost increase.
These and further objects, features and advantages of the present invention will become more readily apparent from the following detailed description of an embodiment of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
The single drawing FIGURE is a side sectional view of a spindle bearing and spindle assembly constructed according to a preferred embodiment of the invention.
DETAILED DESCRIPTION OF THE DRAWING
The vertically arranged spindle 1 of the present invention, for example for a ring spinning machine, comprises a shaft 2 driven to rotate, said shaft 2 being supported in a neck bearing 3 in the form of a roller bearing, and in a two-piece step bearing 4. The neck bearing 3 and the step bearing 4 are located in a bearing housing 5, which has a closed bottom 6.
The bearing housing 5 essentially comprises a tube 7 containing the bottom 6, and a bearing head 9 which takes up the neck bearing 3, which bearing head 9 is inserted from above into the tube 7 by means of a press fit 8. In the inside of the bearing housing 5, an oil bath is located in the area of the step bearing 4.
The step bearing 4 comprises a step bearing tube 11 which takes up the radial forces, and a step bearing 10 comprising a thrust plate 12 which takes up the axial forces. The step bearing tube 11 is supported in a centering tube 13, which in turn is affixed in the bearing head 9 by means of a press fit 14. The centering tube 13 comprises a helically-shaped recess 15, which renders the centering tube 13 flexible to a desired degree.
Between the cylindrical inner contour of the tube 7 and the cylindrical outer contour of the centering tube 13, an annular gap is located, which takes up in a known way an oil spiral 16. The oil spiral 16 is arranged in its entirety in the oil bath. By means of transverse bore holes 18 in the centering tube 13, the annular gap comprising the oil spiral 16 has a connection to the oil bath of the step bearing 4. The oil spiral 16 is supported upwards by means of a spacing tube 17.
The spindle 1, together with a plurality of further adjacently arranged spindles, is affixed in a spindle rail 19, denoted only by a dot-dash line, in a known way. A drive wharve (not shown) is further arranged at the spindle 1, whereby all drive wharves are driven by one drive belt extending in machine longitudinal direction.
With the exception of the diameter of the shaft 2 in the area of the step bearing 4, the bearing shown corresponds to the standard one used in practice. Thus, for example, the distance from the center of the neck bearing 3 to the tip of the shaft 2 at the bearing plate 12 measures 100 mm, to the center of the step bearing tube 11, approximately 94 mm. The diameter of the shaft 2 at the neck bearing 3 usually measures 6.8 mm, the diameter of the shaft 2 just above the step bearing tube 11, that is before the tapering of the shaft 2, measures approximately 6.3 mm. Bearing arrangements with these dimensions seemed to be fully developed, as they have been proven many millions of times over.
After extensive tests it has been now established that the silent running of the spindle 1 can be improved when the diameter of the shaft 2 in the step bearing tube 11 measures 3 to 3.5 mm maximum. Thus, at similar speeds of the spindle 1 as previously, the circumferential speed of the shaft 2 in the step bearing tube 11 can be reduced. A reduced absolute bearing clearance leads no longer to a tearing off of the lubricating film in the step bearing tube 11. Surprisingly, the power required for the drive is reduced at the same time.
Especially in the case of slow spindle speeds it is favorable when the gap between the shaft 2 and the step bearing tube 11 is particularly small. For this reason it is provided in further embodiments that the shaft 2 at the step bearing tube 11 has a slightly spherical form.
The placing of the step bearing tube 11 in a clamped flexible centering tube 13 in close proximity to the neck bearing 3 is not absolutely necessary for the invention. Rathermore it is alternatively possible, in a way not shown, to arrange the step bearing tube 11 in another radially movable way.
The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.

Claims (23)

What is claimed is:
1. A bearing arrangement for spindles in spinning and twisting machines including:
a rotatably supported shaft and a bearing housing with a neck bearing, a step bearing and a radially movable step bearing tube, said bearing tube being arranged in an oil bath, wherein the diameter of the shaft at the step bearing tube measures at the most 0.6 times the diameter of the shaft at the neck bearing, and wherein the diameter of the shaft at the step bearing tube measures approximately 3 to 3.5 mm.
2. A bearing arrangement according to claim 1, comprising a flexible centering tube disposed in the bearing housing and supporting the step bearing tube.
3. A bearing arrangement according to claim 1, wherein the diameter of the shaft measures approximately 6.8 mm at the neck bearing.
4. A bearing arrangement according to claim 2, wherein the diameter of the shaft measures approximately 6.8 mm at the neck bearing.
5. A bearing arrangement according to claim 1, wherein the diameter of the shaft measures approximately 6.3 mm directly above the step bearing tube.
6. A bearing arrangement according to claim 2, wherein the diameter of the shaft measures approximately 6.3 mm directly above the step bearing tube.
7. A bearing arrangement according to claim 3, wherein the diameter of the shaft measures approximately 6.3 mm directly above the step bearing tube.
8. A bearing arrangement according to claim 4, wherein the diameter of the shaft measures approximately 6.3 mm directly above the step bearing tube.
9. A bearing arrangement according to claim 1, wherein a difference in diameter between the shaft at the step bearing tube and the step bearing tube measures 0.015 to 0.035 mm.
10. A bearing arrangement according to claim 9, wherein the difference in diameter between the shaft at the step bearing tube and the step bearing tube measures 0.025 mm to 0.030 mm.
11. A bearing arrangement according to claim 2, wherein a difference in diameter between the shaft at the step bearing tube and the step bearing tube measures 0.015 to 0.035 mm.
12. A bearing arrangement according to claim 11, wherein the difference in diameter between the shaft at the step bearing tube and the step bearing tube measures 0.025 mm to 0.030 mm.
13. A bearing arrangement according to claim 1, wherein the distance from the center of the neck bearing to the step bearing tube measures approximately 94 mm.
14. A bearing arrangement according to claim 2, wherein the distance from the center of the neck bearing to the step bearing tube measures approximately 94 mm.
15. A bearing arrangement according to claim 3, wherein the distance from the center of the neck bearing to the step bearing tube measures approximately 94 mm.
16. A bearing arrangement according to claim 5, wherein the distance from the center of the neck bearing to the step bearing tube measures approximately 94 mm.
17. A bearing arrangement according to claim 9, wherein the distance from the center of the neck bearing to the step bearing tube measures approximately 94 mm.
18. A bearing arrangement according to claim 1, wherein the shaft at the step bearing is slightly spherical in form.
19. A bearing arrangement according to claim 2, wherein the shaft at the step bearing is slightly spherical in form.
20. A bearing arrangement according to claim 3, wherein the shaft at the step bearing is slightly spherical in form.
21. A bearing arrangement according to claim 5, wherein the shaft at the step bearing is slightly spherical in form.
22. A bearing arrangement according to claim 9, wherein the shaft at the step bearing is slightly spherical in form.
23. A bearing arrangement according to claim 13, wherein the shaft at the step bearing is slightly spherical in form.
US09/412,321 1998-12-03 1999-10-05 Bearing for spindles in spinning or twisting machines Expired - Fee Related US6273611B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19865774 1998-12-03
DE19865774 1998-12-03

Publications (1)

Publication Number Publication Date
US6273611B1 true US6273611B1 (en) 2001-08-14

Family

ID=7893335

Family Applications (1)

Application Number Title Priority Date Filing Date
US09/412,321 Expired - Fee Related US6273611B1 (en) 1998-12-03 1999-10-05 Bearing for spindles in spinning or twisting machines

Country Status (1)

Country Link
US (1) US6273611B1 (en)

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2704946A (en) * 1952-03-29 1955-03-29 Universal Winding Co Textile spindle
US2757992A (en) * 1953-02-10 1956-08-07 Skf Kugellagerfabriken Gmbh Bearing device
US2973229A (en) * 1951-02-22 1961-02-28 Skf Kugellagerfabriken Gmbh Bearing units for spindles of spinning and twisting frames
US3500624A (en) * 1968-04-25 1970-03-17 Lev Judelevich Polyakovsky Twisting and forming device for pneumatic and mechanical spinning
US3510181A (en) * 1967-08-16 1970-05-05 Schurr Stahlecker & Grill Spindle bearing for a spinning or twisting machine
US4875334A (en) * 1987-11-19 1989-10-24 Zavody Na Vyrobu Lozisk, Povazska Bystrica Spindle construction for mounting arrangements for spinning machine rotors
US4997291A (en) * 1988-11-26 1991-03-05 Fritz Stahlecker Bearing for spindles of spinning or twisting machines
US5119620A (en) * 1990-05-17 1992-06-09 Wilhelm Stahlecker Gmbh Holding arrangement for a spindle of ring spinning or ring twisting machines
US5182901A (en) * 1989-06-20 1993-02-02 Hans Stahlecker Spinning or twisting spindle arrangement
US5528892A (en) * 1993-07-28 1996-06-25 Gebruder Loepfe Ag Flexible textile spindle assembly
US5996326A (en) * 1997-06-20 1999-12-07 Novibra Gmbh Spindle for a spinning or a twisting machine

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2973229A (en) * 1951-02-22 1961-02-28 Skf Kugellagerfabriken Gmbh Bearing units for spindles of spinning and twisting frames
US2704946A (en) * 1952-03-29 1955-03-29 Universal Winding Co Textile spindle
US2757992A (en) * 1953-02-10 1956-08-07 Skf Kugellagerfabriken Gmbh Bearing device
US3510181A (en) * 1967-08-16 1970-05-05 Schurr Stahlecker & Grill Spindle bearing for a spinning or twisting machine
US3500624A (en) * 1968-04-25 1970-03-17 Lev Judelevich Polyakovsky Twisting and forming device for pneumatic and mechanical spinning
US4875334A (en) * 1987-11-19 1989-10-24 Zavody Na Vyrobu Lozisk, Povazska Bystrica Spindle construction for mounting arrangements for spinning machine rotors
US4997291A (en) * 1988-11-26 1991-03-05 Fritz Stahlecker Bearing for spindles of spinning or twisting machines
US5182901A (en) * 1989-06-20 1993-02-02 Hans Stahlecker Spinning or twisting spindle arrangement
US5119620A (en) * 1990-05-17 1992-06-09 Wilhelm Stahlecker Gmbh Holding arrangement for a spindle of ring spinning or ring twisting machines
US5528892A (en) * 1993-07-28 1996-06-25 Gebruder Loepfe Ag Flexible textile spindle assembly
US5996326A (en) * 1997-06-20 1999-12-07 Novibra Gmbh Spindle for a spinning or a twisting machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Suessen-Novibra Technical Information SCT 6114 ND, Technologie der Spindel HP-S 68. 09/95.

Similar Documents

Publication Publication Date Title
US4773210A (en) Open-end rotor-spinning device
GB2329511A (en) Spindle motor with fluid dynamic bearing having a journal in combination with a conical bearing (one side open)
EP1113567A4 (en) Spindle motor
US6988980B2 (en) Separator with bearing lubrication arrangement
US4844625A (en) Structure of journal bearing for motor operating at high revolutionary speeds
US6939046B2 (en) Hydrodynamic bearing, spindle motor and hard disk drive
US6273611B1 (en) Bearing for spindles in spinning or twisting machines
US6035620A (en) Twisting spindle, especially two-for-one or direct cabling spindle
EP1903230B1 (en) Rolling bearing apparatus
US6552455B1 (en) Hydrodynamic bearing and spindle motor
US6826899B2 (en) Rotor shaft for an open-end spining rotor
KR100715025B1 (en) A spindle motor having a hydrodynamic bearing
JP3574266B2 (en) Shaft bearing structure of small motor
US5887417A (en) Open-end spinning apparatus with a spinning rotor driven by a single motor
JPH06288411A (en) Thrust bearing device
AU2338800A (en) Device of a tool spindle
KR930020046A (en) Bearing device for shaft of hollow spindle
US5992137A (en) Supporting disc for a supporting disc bearing of open-end spinning rotors and process of making same
CN217462887U (en) Bidirectional roller combined bearing assembled on direct-drive vertical mill
US4681492A (en) High-speed spindle
JPH02145820A (en) Bearing device for spindle of fine spinning or yarn twisting machine
CN113164967B (en) Device for grinding fibrous material suspensions
CN113124166B (en) Sealing structure
US6186666B1 (en) Ring spindle and process for lubricating same
CN113775644A (en) Bidirectional roller combined bearing assembled on direct-drive vertical mill

Legal Events

Date Code Title Description
AS Assignment

Owner name: STAHLECKER, FRITZ, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:STAHLECKER, GERD;REEL/FRAME:010302/0788

Effective date: 19990924

Owner name: STAHLECKER, HANS, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:STAHLECKER, GERD;REEL/FRAME:010302/0788

Effective date: 19990924

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

AS Assignment

Owner name: NOVIBRA GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:STAHLECKER, FRITZ;STAHLECKER, HANS;REEL/FRAME:021040/0385;SIGNING DATES FROM 20061206 TO 20070208

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
LAPS Lapse for failure to pay maintenance fees

Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20090814